KR101128012B1 - Clutch device, motor apparatus and wiper system - Google Patents

Abstract

According to the present invention, the input disks 28, 128, 228 and the clutch disks 38, 64 do not generate relative rotation between the input disks 28, 128, 228 and the clutch disks 38, 64, 238. 238 is possible only when the output shaft 12 is located at a single engageable point e within the normal reciprocating rotational angle range X of the output shaft 12. When the load acting on the output shaft 12 is equal to or greater than a predetermined value, the input disks 28, 128, 228 and the clutch disks 38, 64, 238 are disengaged from each other, so that the input disk ( Relative rotation occurs between 28, 128, 228 and clutch disks 38, 64, 238. FIG.

Clutch device, motor device, wiper system, input disc, clutch disc, relative rotation

Description

Clutch, Motor and Wiper System {CLUTCH DEVICE, MOTOR APPARATUS AND WIPER SYSTEM}             

1 is a perspective view showing a wiper motor device and a clutch device according to a first embodiment of the present invention.

Figure 2 is a perspective view showing a part of the wiper motor device and the clutch device according to the first embodiment of the present invention.

Figure 3 is an exploded perspective view showing a wiper motor device and a clutch device according to a first embodiment of the present invention.

4 is a plan sectional view showing the configuration of the wiper motor apparatus according to the first embodiment of the present invention.

FIG. 5 is a sectional view taken along the line VV of FIG. 4, showing the configuration of the wiper motor apparatus according to the first embodiment of the present invention. FIG.

6 is a plan sectional view showing the configuration of the wiper motor apparatus according to the first embodiment of the present invention.

FIG. 7 is a sectional view taken along the line VII-VII of FIG. 6, showing the wiper motor apparatus according to the first embodiment of the present invention. FIG.                 

FIG. 8 is a cross-sectional view of the wiper motor apparatus according to the first embodiment of the present invention corresponding to FIG. 7 in a clutch released state; FIG.

9 is an exploded perspective view showing the configuration of the clutch device according to the first embodiment of the present invention.

10 is an exploded perspective view of the clutch device according to the first embodiment of the present invention.

Fig. 11 is a perspective view showing main parts of a wiper motor device and a clutch device according to the first embodiment of the present invention.

FIG. 12 is a perspective view showing the configuration of main parts of the wiper motor apparatus and the clutch apparatus according to the first embodiment corresponding to FIG.

Fig. 13 is a schematic view for explaining an angle setting for automatically resetting the clutch device of the wiper motor device according to the first embodiment of the present invention to its initial position.

Fig. 14 is a schematic plan view illustrating an operation for automatically resetting the clutch device of the wiper motor device according to the first embodiment of the present invention to its initial position.

Fig. 15 is a schematic plan view illustrating an operation for automatically resetting the clutch device of the wiper motor device according to the first embodiment of the present invention to its initial position.

Fig. 16 is a schematic plan view illustrating an operation for automatically resetting the clutch device of the wiper motor device according to the first embodiment of the present invention to its initial position.

Fig. 17 is a schematic plan view illustrating the operation for automatically resetting the clutch device of the wiper motor device according to the first embodiment of the present invention to its initial position.

Fig. 18 is a schematic plan view illustrating an operation for automatically resetting a clutch device of a wiper motor device according to the first embodiment of the present invention to its initial position.

19 is an exploded perspective view showing a modified form of the clutch device according to the first embodiment of the present invention.

20 is an exploded perspective view showing the configuration of the clutch device according to the second embodiment of the present invention.

Fig. 21 is a plan view showing the construction of a motor apparatus according to the third embodiment of the present invention.

Fig. 22 is a sectional view showing an entire structure of a wiper motor device with a clutch device according to a fourth embodiment of the present invention.

Figure 23 is an exploded perspective view showing the configuration of the clutch device according to the fourth embodiment of the present invention.

24 is an exploded perspective view showing the configuration of the clutch device according to the fourth embodiment of the present invention;

* Description of the symbols for the main parts of the drawings *

10: clutch device 12: output shaft

14: rotational restraint unit 16: fall prevention unit

18: relative rotation shaft 20: clutch base

24, 26: male fitting portion 28, 128, 228: input disk

34, 36: male engagement portion 38, 64, 238: clutch disc

42: base wall 44: peripheral wall                 

46 and 48: arm fitting guide portions 50 and 52: arm fitting portions

54: accommodating part 56: wave washer (elastic member)

96: housing 142: stopper protrusion

144: first rotation limit unit 146: second rotation limit unit

The present invention relates to a clutch device, a motor apparatus and a wiper system.

For example, a wiper system for wiping a window pane of a vehicle includes a motor device as a power source of the wiper system.

The wiper motor device, in particular the rear wiper motor device, comprises a worm wheel; It includes a swing arm and a joint member. The worm wheel meshes with a rotating shaft of an armature which is rotatably supported by the case. The swing arm is connected to the wiper shaft. One end of the joint member is connected to a predetermined point of the worm wheel, and the other end is connected to the swing arm. As the current is applied to the wiper motor device, the armature is rotated to rotate the worm wheel. Then, the rotation of the worm wheel is switched to the swinging motion of the swing arm through the joint member to reciprocally rotate the wiper shaft. Thus, the wiper arm mounted directly on the wiper shaft swings to wipe the rear pane of the vehicle. One such wiper motor device has been proposed in Japanese Patent Laid-Open No. 09-118202.

When the wiper is not in operation, ie when the wiper blades connected to the wiper arm are stopped and thus remain approximately parallel to the lower edge of the windowpane, external forces, for example a large amount of snow When an external force pressurized by the force acts on the wiper blade and the wire arm, the wiper blade and the wiper arm are pressed downward more than the lower turning point. At this time, the wiper shaft and the swing arm of the wiper motor device is rotated more than the normal reciprocating rotation angle range. Therefore, the joint member connected to the swiss arm or the worm wheel connected to the joint member may be damaged by the external force.

Therefore, in the wiper motor apparatus of Japanese Patent Laid-Open No. 09-118202, in order to prevent damage to the joint member or the worm wheel and to prevent rotation of the wiper arm to the vehicle body region exceeding the window glass surface of the vehicle, the swing A rotation range limitation is provided at a position outside the normal reciprocation angle range of the swing arm to limit the rotation of the swing arm beyond the predetermined reciprocation angle range of the arm.

However, for example, even when the wiper blade and the wiper arm are not located outside the predetermined reciprocating rotation angle range, excessive external force may be applied to the wire blade and the wiper arm. In other words, even when the wiper blade and the wiper arm operate within a predetermined reciprocating rotation angle range (normal wiping range), excessive external force can be applied to the wiper blade and the wiper arm. This can occur when a large amount of snow that has accumulated on the roof of the vehicle falls into the wiper blades and wiper arms that are operated and positioned in the usual wiping range other than the lower inversion point. In this case, the wiper blade and the wiper arm are stopped by a large amount of fallen snow or are subject to excessive external force from the fallen snow. Thus, excessive external force is applied through the wiper shaft to the swing arm, joint member, worm wheel and / or worm gear, so that these components can be damaged by excessive external force. Therefore, the problem of such breakage still exists.

Therefore, in the case of the wiper motor apparatus proposed in Japanese Patent Laid-Open No. 09-118202, each component of the wiper motor apparatus needs to be designed to withstand the excessive external force described above.

It has been proposed to provide a friction clutch device on the output shaft (wiper shaft) in order to prevent damage to the corresponding components of the wiper motor device such as the worm wheel even when excessive external force is applied. However, such a friction clutch device has a problem of significantly lowering the transmission efficiency of the rotational force. In addition, there is a problem that noise is generated due to the friction sliding movement of the clutch. In addition, since the operating point of the friction clutch device depends largely on the frictional force of the friction clutch device, the operating point of the friction clutch device may vary from product to product.

In order to solve these problems, a wiper motor including a swing device, a deceleration device and a motor body when excessive external force is applied while the wiper blade and the wiper arm are operated in a normal rotational angle range (in-situ wiping motion). In order to protect the overall configuration of the device, it may be considered to provide a clutch that is engaged through the output shaft. In this type of clutch operated through engagement, even when the output shaft is locked, damage to the corresponding component of the wiper motor device can be prevented and damage to the wiper motor device can be prevented. In addition, the loss of rotational force is reduced by friction sliding movement, and the transmission efficiency of rotational force is increased. The generation of noise is also prevented.

However, in the case of such a clutch operated through a toothing, when an excessive external force (overload) is applied to the clutch, the clutch is released. When the clutch is disengaged, relative rotation, i.e. idling, occurs between the output shaft (drive side component) and the worm wheel (drive side component or motor side component). Therefore, the wiping position of the wiper arm fixed to the output shaft is controlled, for example, by an automatic stop provided on the worm wheel (drive side component or motor side component) to automatically stop the wiper arm at a predetermined stop position. If so, when an excessive external force is applied to the clutch to release the engagement, the predetermined stop position of the wiper arm is shifted. Therefore, there is a problem that the wiper arm does not automatically stop at a predetermined stop position.

Therefore, the present invention has been proposed to solve the above problems, it is possible to prevent the damage of the respective components of the clutch device, the motor device and the wiper system, to prevent the damage of the motor device, the output shaft ( The output shaft (drive side component) is moved to the motor side component (drive side) at a predetermined point so that normal operation can be performed even when relative rotation occurs between the driven side component and the motor side component (drive side component). It is an object of the present invention to provide a clutch device, a motor device and a wiper system capable of automatically returning the clutch device to its initial position by operating the motor side component (drive side component) to reconnect to the component part).

In order to achieve the above object, the present invention provides a clutch device including a first rotating member, a second rotating member, an output shaft, and one or more rotating limiters. The first rotating member is rotatably rotated by the driving force provided thereto. The second rotating member is rotated at the maximum rotational coupling force so that the first rotating member rotates integrally with the first rotating member without a relative rotation occurring between the first rotating member and the second rotating member when the first rotating member is reciprocated. It is made to be engageable with the member. The output shaft is connected to the second rotating member to be integrally rotated with the second rotating member. The output shaft is capable of normal rotation within a predetermined normal reciprocation rotation angle range. The one or more rotational limitations limit the reciprocation of the output shaft beyond a limit angle range greater than the normal reciprocation angle range of the output shaft. Initial coupling between the first and second rotary members at the maximum rotational coupling force that does not cause relative rotation between the first and second rotary members is such that the output shaft is within the normal reciprocal angle range of the output shaft. Only possible if it is located at a single coupling point. When the load acting as the output shaft is greater than or equal to a predetermined value, the first rotating member and the second rotating member are disengaged from each other so that relative rotation occurs between the first rotating member and the second rotating member.

In addition, the present invention provides a motor device including the clutch device, the housing and the motor body in order to achieve the above object. The housing houses a clutch device. The motor body is connected to the clutch device to supply a driving force to the first rotating member of the clutch device.

In addition, the present invention to achieve the above object, provides a wiper system including the above-described clutch device, housing, wiper and motor body. The housing houses a clutch device. The wiper is directly or indirectly connected to the output shaft of the clutch device, and swings reciprocally at the time of reciprocating the output shaft.

Further objects, features and advantages of the present invention can be more clearly understood from the following detailed description and the accompanying drawings.

(Embodiment 1)

1 and 2 are perspective views showing the overall configuration of a wiper motor apparatus 90 in which a clutch device 10 according to a first embodiment of the present invention is installed. The wiper motor device 90 is formed as a wiper drive motor for driving a vehicle wiper system, and the clutch device 10, the motor body 92 and a motion converting mechanism (also referred to as a swing device). (94).

The clutch device 10 includes an output shaft 12. The base end (rear end) of the output shaft 12 includes a rotation restraint portion 14, a fall prevention portion 16, and a relatively rotatable relative rotation shaft portion 18. The rotational restraint portion 14 includes a protrusion 14a protruding in the axial direction. The fall prevention portion 16 is formed at the rear end of the rear end of the output shaft 12. The relative rotation shaft portion 18 is disposed between the rotational restraint portion 14 and the fall prevention portion 16.

A clutch base (base member) is fixed to the rotational restraint portion 14 of the output shaft 12 by, for example, press fitting. The clutch base is formed of a disc body and has a support hole 22 at its center. The support hole 22 is fixed to the rotation restraint unit 14, and the clutch base 20 is integrally rotated with the output shaft 12. In addition, male fitting portions 24 and 26 are disposed to face each other in the circumferential direction of the clutch base 20, that is, the male fitting portions 24 and 26 are formed of a clutch base ( It is located at a position 180 degrees apart from each other in the circumferential direction of the 20, and is provided on the outer peripheral portion of the clutch base 20 in a manner that projects in the radial direction of the output shaft (12). The radial extension of the male fitting portion 24 on one side is larger than the radial extension of the male fitting portion 24 on the other side. The male fitting portions 24 and 26 correspond to the clutch disk 38 to be described later.

The fall prevention unit 16 of the output shaft 12 is provided with an input disk (first rotation member) 28. The input disk 28 is formed of a gear body or a gear member, and has a shaft hole 30 in the center thereof. The fall prevention portion 16 of the output shaft 12 is accommodated through the shaft hole 30, and the fall prevention clip on the fall prevention portion to prevent the fall of the input disk 28 from the output shaft 12 ( 32) is installed. Therefore, the input disk 28 is coaxial with the output shaft 12 and the output disk 28 is rotatable about the output shaft 12 without being separated in the axial direction of the output shaft 12. It is supported by the output shaft 12 at one shaft end side of the shaft 12. When a driving force is input to the input disk 28, the input disk 28 is rotated about the axis of the output shaft 12. Two pairs (first and second pairs) of numerical engagement portions from the end face of the input disk 28 (the clutch base 20 side, that is, the other end in the axial direction of the output shaft 12) to the clutch base 2 side ( Male mating portions 34 and 36 protrude.

One pair of engagement portions (first pair of engagement portions) 34 of the two pairs of male engagement portions 34 and 36 are disposed to face each other in the circumferential direction. That is, they are located at positions 180 degrees apart from each other in the circumferential direction. In addition, the other pair of engaging portions (second pair of engaging portions) 36 of the two pairs of male engaging portions 34 and 36 are disposed to face each other in the circumferential direction. That is, it is located at a position 180 degrees apart in the circumferential direction. In addition, the male pressure portion 34 on one side and the male portion 36 on the other side are arranged at the same interval (interval of 90 degrees in the circumferential direction). One pair of teeth 34 of the two pairs of teeth 34 and 36 is connected to the other pair of teeth 36 of the two pairs of teeth 34 and 36 in the radial direction of the input disk 28. It is located outside the excess and extends to the teeth of the input disk 28. In addition, the two pairs of teeth 34 and 36 correspond to the clutch disk 38 to be described later.

The clutch disc (second rotating member) 38 is supported by the relative rotating shaft portion 18 of the output shaft 12. The clutch disk 38 is formed in a cup shape and includes a base wall 42 and a peripheral wall 44. The shaft hole 40 corresponding to the shaft 12 is formed through the base wall 42. The peripheral wall 44 extends in the axial direction of the output shaft 12 from the outer circumference of the base wall 42. When the output shaft 12 (more specifically, the relative rotation shaft portion 18) is received through the shaft hole 40, the clutch disk 38 is the output shaft 12 and the input disk 12. It is coaxial with and is located at the other end side (clutch base 20 side) of the output shaft 12 with respect to the input disk 28, and the output shaft 12 by the output shaft 12 in the axial direction Is supported to be movable.

Female fitting guide portions 46 and 48 are provided on the open side peripheral portion of the peripheral wall 44 so as to correspond to the male fitting portions 24 and 26 of the clutch base 20. The clutch base 2 may be moved between the male fitting portions 24 and 26 and the female fitting guide portions 46 and 48 of the clutch base 2 in the axial direction of the output shaft 12. The male fitting portions 24 and 26 of the 20 are fitted to the female fitting guide portions 46 and 48 of the peripheral wall 44 in the axial direction of the output shaft 12, respectively. Accordingly, the clutch disc 38 rotates with the clutch base 20 (ie, the output shaft 12) and is movable relative to the clutch base 20 in the axial direction of the output shaft 12.

Two pairs of female engagement portions (second side engagement portions) 50 and 52 are arranged on the rear surface of the base wall of the clutch disc 38 (ie, the one side end portion of the output shaft 12). Is formed in a groove shape.                     

The female engagement portions 50 and 52 correspond to the male engagement portions 34 and 36 of the input disk 28, respectively. One pair of female engagement portions (the first pair of female engagement portions) 50 of the two pairs of female engagement portions 50 and 52 are positioned to face each other in the circumferential direction. That is, they are located at positions 180 degrees apart from each other in the circumferential direction. In addition, the other pair of female engagement portion (second pair of female engagement portion) 52 of the female engagement portion (50, 52) of the two thinning is positioned to face each other in the peripheral direction. That is, they are located at positions 180 degrees apart from each other in the circumferential direction. Further, the first pair of female engagement portions 50 and the second pair of female engagement portions 52 are arranged at equal intervals (that is, at intervals of 90 degrees in the circumferential direction). The male engaging portion 34 of the input disk 28 may be engaged with the female engaging portion 50 of the clutch disk 38, and the male engaging portion 36 of the input disk 28 may be the clutch disk 38. ) Can be engaged with the fitting portion 52. In this way, when the input disk 28 is rotated, the rotational force of the input disk 28 is transmitted to the clutch disk 38, the clutch disk 38 is rotated together with the input disk 28. In addition, as will be described later, the numerical engagement portions 34 and 36 of the input disk 28 are only at a predetermined single engagement point (about 170 degrees in this embodiment) of the normal reciprocating rotation angle range X of the output shaft 12. Engagement with one corresponding mating portion 50, 52 of the clutch disc 38 (FIGS. 14-18). In other words, each of the male engagement portions 34 does not engage with each of the female engagement portions 52, and each of the male engagement portions 36 does not engage with each of the female engagement portions 50.

Inclined surfaces are formed on the sidewalls 34a and 36a of the male engaging portions 34 and 36 of the input disk 28 and the sidewalls 50a and 52a of the female engaging portions 50 and 52 of the clutch disk 38. . In other words, each male engagement portion 34, 36 has a trapezoidal cross section, and each female engagement portion 50, 52 has a corresponding trapezoidal cross section. When the input disk 28 is rotated as described above, the rotational force is transmitted from the input disk 28 to the clutch disk 38, and thus the clutch base in the axial direction of the output shaft 12 in the clutch disk 38. Force component is generated to the side of (20).

Both the side walls 34a and 36a of the male engaging portions 34 and 36 of the input disk 28 and the side walls 50a and 52a of the female engaging portions 50 and 52 of the clutch disk 38 are inclined as described above. It is not necessary to have a. In other words, only one of the side walls 34a and 36a of the respective mating portions 34 and 36 may be formed of an inclined surface that is inclined in the peripheral direction or inclined with respect to the peripheral direction. In addition, only one sidewall of the sidewalls 50a and 52a of the female engagement portions 50 and 52 may be formed as an inclined surface inclined in the peripheral direction or inclined in the peripheral direction. Even with such a configuration, a partial force may be generated in the clutch disc 38 toward the clutch base 20 in the axial direction of the output shaft 12 by transmission of the rotational force from the input disc 28 to the clutch disc 38. Can be.

In addition, the inner space formed by the inner side of the clutch disk 38, that is, the base wall 42 and the peripheral wall 44 forms a receiving portion 54. The clutch base 20 is fitted to the open side peripheral portion of the peripheral wall 44 of the clutch disc 38, so that the clutch base 20 closes the receiving portion 54.

The receiving portion 54 accommodates a plurality of wave washers 56 (two in this embodiment) provided as the elastic member of the present invention. The wave washer 56 is disposed between the clutch disc 38 (base wall 42) and the clutch base 20. In addition, the wave washer 56 is output from a mating state in which the male mating portions 34 and 36 of the input disk 28 and the female mating portions 50 and 52 of the clutch disk 38 rotate together. A predetermined resistance force (wave washers 56 along the axial movement of the clutch disc 38) against the axial movement of the clutch disc 38 to the axial end side of the shaft 12 (the clutch base 20 side). Restoring force generated by elastic deformation). In other words, in normal operation, the male engagement portions 34 and 36 of the input disc 28 are engaged, i.e. received, with the female engagement portions 50 and 52 of the clutch disc 38, and the wave washer 56 ) Maintains the engagement state between the male engagement portions 34 and 36 of the input disc 28 and the female engagement portions 50 and 52 of the clutch disc 38. When the male engaging portions 50 and 52 of the input disk 28 are to be disengaged from the female engaging portions 50 and 52 of the clutch disk 38, the clutch disk 38 moves toward the clutch base 20 side. Trying to axially move, the wave washer 56 exerts a pressing force (restoring force) on the axial movement of the clutch disc 38.

In normal operation (i.e., the state in which the clutch disc 38 does not try to axially move toward the clutch base 20 side), the wave washer 56 applies an appropriate pressing force between the clutch base 20 and the clutch disc 38. Can always be added. In addition, the wave washer 56 is intended to be released from the female engagement portions 50 and 52 only when the clutch disc 38 tries to move toward the clutch base 20 side. Only when it is possible to apply a greater pressing force (restoration force).

The clutch device 10 having the above-described configuration is accommodated in the housing 96, and the output shaft 12 protrudes outward from the housing 96.                     

In addition, the male fitting portion 26 and the corresponding housing 96 have a stopper protrusion 142 protruding from the clutch base 20 of the clutch device 10 longer in the radial direction than the male fitting portion 24. ) Is formed.

The stopper protrusion 142 is formed of an arcuate body and is positioned in a rotation path of the male fitting portion 26 to which the male fitting portion 26 moves while the clutch base 20 rotates. . One side peripheral end of the stopper protrusion 142 forms a first rotation limiter 144, and the other peripheral portion of the stopper protrusion 142 forms a second rotation limiting part 146. When the male fitting portion 26 is constrained by the first rotation limiting portion 144 or the second rotation limiting portion 146 of the stopper protrusion 142, further rotation of the clutch base 20 is limited. . Therefore, when the clutch base 20 (output shaft 12) rotates together with the clutch disk 38 as the rotation driving force of the input disk 28 is transmitted to the clutch base 2, the male fitting portion When 26 is constrained by the first rotation limiting portion 144 or the second rotation limiting portion 146 of the stopper projection 142, further rotation of the clutch base 20 (output shaft 12) is It is forcibly limited. Accordingly, relative rotation occurs between the input disk 28 and the clutch base 20.

The rotation angle range of the male fitting portion 26 between the first rotation limiting portion 144 and the second rotation limiting portion 146 of the stopper protrusion 142 (that is, the rotation angle range of the output shaft 12) is The limit angle range Y is set. More specifically, the limit angle range Y is set to be larger or wider than the normal reciprocation angle range X of the output shaft 12 (clutch base 20 and clutch disc 30). The limit angle range Y in this embodiment is set to be 180 degrees.

As described above, the male engagement portion 34 on one side is positioned beyond the male engagement portion 36 on the other side in the radial direction of the input disk 28. Therefore, the male engagement portion 34 on one side is not engaged with the female engagement portion 52 corresponding to the male engagement portion 36 on the other side. Similarly, the male engagement portion 36 on the other side is not engaged with the female engagement portion 50 corresponding to the male engagement portion 34 on one side. In addition, the number engagement portion 34 on one side is positioned to face each other in the peripheral direction of the input disk 28, the other number engagement portion 36 on the other side is positioned opposite to each other in the peripheral direction of the input disk 28. . Therefore, when the limiting angle range Y larger than the normal reciprocating rotational angle range X of the output shaft 12 is set to about 180 degrees, the respective engagement portions 34 and 36 of the input disc 28 are output shafts. Only one of the female engagement portions 50, 52 of the clutch disc 38 can be engaged with the corresponding one of the female engagement portions at the predetermined single engagement point in the normal reciprocating rotation angle range X of (12). That is, as schematically shown in Fig. 13, this predetermined single engagement point set within the normal reciprocating rotational angle range X is located within a corresponding angular range starting from at least one of the peripheral ends a, b of the limiting angle range Y, The normal reciprocating rotational angle of the output shaft 12 has the same extension angle as doc. More specifically, the angle? Between the engaging point e and the end a or the end b of the limiting angle range Y is set smaller than the reciprocating rotational angle docdoc of the output shaft 12. Therefore, the relative between the input disk 28 and the clutch disk 38 in accordance with the engagement between the male engaging portion 34, 36 of the input disk 28 and the female engaging portion 50, 52 of the clutch disk 38. Initial rotation between the input disk 28 and the clutch disk 38 at maximum rotational engagement force without rotation occurs allows the output shaft 12 to engage a single engagement within the normal rotational angle range X of the output shaft 12. Only possible if it is located at a point.

Further, as described above, when the male engaging portions 34 and 36 of the input disk 28 are accommodated in the female engaging portions 50 and 52 of the clutch disk 38, that is, the female engaging portions 50 and 52. ), The rotational force is transmitted from the input disk 28 to the clutch disk 38. In addition, the disengaged state where the male engaging portions 34 and 36 of the input disk 28 are disengaged from the female engaging portions 50 and 52 of the output disk 38, that is, the clutch disk 38 is engaged. Even in the state where the axial position is moved from the first axial position to the clutch base 20 which is the disengaged position (second axial position), the clutch disk 38 rotates together with the input disk 28. Preferably, a predetermined frictional force is generated between the engagement portions 34 and 36 of the input disk 28 and the base wall 42 of the clutch disk 38 due to the pressing force (restoration force) of the wave washer 56. During this rotation, reduced rotation is less than the maximum engagement force achieved through the engagement between the male engagement portions 34, 36 of the input disc 38 and the female engagement portions 50, 52 of the clutch disc 38. The clutch disk 38 is engaged with the input disk 28 in the engaging force. As described above, even when the male engaging portions 34 and 36 and the female engaging portions 50 and 52 are disengaged, the friction force of the wave washer 56 is reduced by the rotational coupling force of the input disk 28. Together with the clutch disc 38 is set to achieve this rotation. The yoke housing 98 of the motor body 92 has a flat shaft having one end portion formed by a drawing process and having a predetermined cross section extending in a direction orthogonal to the axis of the rotary shaft 110. It is formed into a cylindrical housing in the form. The transverse direction of the predetermined cross section of the flat cup-shaped cylindrical housing coincides with the axial direction of the output shaft 12. The opening of the yoke housing 98 is integrally connected to the housing 96. A bearing 102 is disposed on the base wall 100 of the yoke housing 98. An end housing 104 made of an insulating resin is fixed to the other end of the yoke housing 98.

A bearing 106 is disposed at the center of the end housing 104. The rotating shaft 110 of the armature 108 is supported by the bearing 106 of the end housing 104 and the bearing 102 of the yoke housing 98, the armature 108 is yoke housing 98 Is accommodated in. A magnet 112 is fixed to the inner circumferential wall of the yoke housing 98, and the magnet 102 is positioned to face the armature 108.

The plurality of brushes 114 are each held by a brush case in the end housing 104. Each brush 114 is formed in a rectangular bar and is pressed against the commutator 116 of the armature 108. A connecting pigtail 118 extends from each brush 114, and the tip of the pigtail 118 is connected to a corresponding power supply connection line.

The rotating shaft 110 of the motor body 92 (an armature 018) is connected to the worm gear 122 of the motion converter 94 through a coupling (coupling) (120).

One end of the worm gear 122 is rotatably supported by the housing 96 through a bearing 124. The other end of the worm gear 122 is rotatably supported by the housing 96 through the bearing 126. The worm gear 122 is meshed with the worm wheel 128.                     

The worm wheel 128 is meshed with the worm gear 122 and received in the housing 96. The worm wheel 128 is rotated with respect to the rotary shaft 130, and extends in a direction orthogonal to the axis of the worm gear 122 (rotating shaft 120).

A sector gear 132 provided as a swing member is connected to the worm wheel 128. 11 and 12, one end of the sector gear 132 is rotatably supported by a support shaft 134. The support shaft 134 is provided at a corresponding point of the worm wheel 128 that is different from the corresponding point of the rotary shaft 130, that is, moved radially from the rotary shaft 130. A gear tooth 136 is formed at the other end of the sector gear 132, and the gear tooth 136 meshes with the input disk 28 of the clutch device 10. One end of a holding lever 138 is connected to the sector gear 132 through a support shaft 140. The other end of the retaining lever 138 is rotatably connected to the center of rotation of the input disk 28, that is, the output shaft 12. As such, the shaft-to shaft pitch between the support shaft 140 and the output shaft 12 is maintained, and the engagement state between the sector gear 132 and the input disk 28 is maintained. Therefore, when the worm wheel 128 rotates, the sector gear 132 is swinged to reciprocally drive the input disk 28.

The rear side of the housing 96 in which the clutch device 10 and the motion converter 94 are accommodated is closed by a cover plate 148.

For example, the sliding member 147 made of a resin material is connected to the holding lever 138 side, that is, the side opposite to the sector gear 132. The sliding member 147 is slidably engaged with the cover plate 148. With this configuration, the movement of the retaining lever 138 in its thickness direction (axial direction of the output shaft 12) is limited.

A portion of the output shaft 12 protruding outward from the housing 96 is directly connected to the wiper W (Figs. 14 to 18). The wiper W is reciprocally driven by the reciprocating rotation of the output shaft 12. In this case, the fixed strength in the rotational direction between the output shaft 12 (rotational confinement portion 14) and the clutch base 20 (support hole 22) is the output shaft 12 in the rotational direction. It is set larger than the connection strength of the wiper (W) of the furnace.

The wiper W does not need to be directly connected to the output shaft 12, but may be indirectly connected to the output shaft 12 through, for example, a link or a rod.

Next, the operation according to the first embodiment of the present invention will be described.

In the wiper motor device 90, when the motor body 92 (an armature 108) rotates, the rotational force is transmitted to the worm wheel 128 through the worm gear 122, the worm wheel 128 is rotated. When the worm wheel 128 rotates, the sector gear 132 connected to the worm wheel 128 swings. The swing movement of the sector gear 132 reciprocates the input disk 28.

In the normal operating state, the male engagement portions 34 and 36 of the input disc 28 of the clutch device 10 engage with the female engagement portions 50 and 52 of the clutch disc 38, that is, the clutch disc 38. Fitting with the female engagement portions (50, 52). Therefore, the clutch disk 38 is coupled with the input disk 28 at the maximum rotational coupling force without relative rotation between the input disk 28 and the clutch disk 38. In this state, even if the clutch disc 38 tries to move between the male engagement portions 34 and 36 and the female engagement portions 50 and 52 so as to release the engagement, the clutch disc 38 from the wave washer 56 is removed. A predetermined resistance force is applied. Therefore, the engagement between the male engagement portions 34 and 36 and the female engagement portions 50 and 52 is maintained. Relative axial movement of the output shaft 12 in the axial direction between the male fitting portions 24 and 26 of the clutch base 20 and the female fitting guide portions 46 and 48 of the clutch disc 38 is achieved. In an enabling manner, the male fitting portions 24, 26 of the clutch base 20 are fitted to the female fitting guide portions 46, 48 of the clutch disc 38, respectively. Thus, as shown in Figs. 5, 7 and 11, the clutch device 10 is in an engaged state. In this coupled state, when the input disk 28 reciprocates, the rotational driving force is transmitted from the input disk 28 to the clutch disk 38 through the male engaging portions 34 and 36 and the female engaging portions 50 and 52. Is passed to. Since the clutch disc 38 meshes with the clutch base 20 fixed to the output shaft 12, the rotational driving force transmitted to the clutch disc 38 is transmitted from the clutch disc 38 to the clutch base 20. do. Thus, the output shaft 12 is rotated together with the clutch disc 38 and the clutch base 20.

As such, the wiper W connected to the output shaft 12 is reciprocally driven in accordance with the reciprocating rotation of the output shaft 12.

In the wiper motor apparatus 90 in a normal operating state (rotation state), when the rotation driving force is transmitted from the input disk 28 of the clutch device 10 to the output shaft 12, the rotation driving force is related. It can be transmitted without generating any sliding motion in the components. In other words, the clutch disc 38 is engaged from the engaged state to maintain the engaged state between the male engagement portions 34 and 36 of the input disc 28 and the female engagement portions 50 and 52 of the clutch disc 38. The resistance of the wave washer 56 applied to the clutch disc 38 to limit its axial movement is not consumed as frictional force. Therefore, the fall of the rotation transfer efficiency can be prevented remarkably. Further, since the rotational driving force can be transmitted without generating any sliding motion in the related components, noise generation that can be generated by the sliding movement of the related components can be prevented.

Further, as described above, the clutch disc from the engaged state to maintain the engaged state between the male engagement portions 34, 36 of the input disc 28 and the female engagement portions 50, 52 of the clutch disc 38. The resistance force of the wave washer 56 applied to the clutch disc 38 to limit the axial movement of the 38 is supported by the clutch base 20 fixed to the output shaft 12, and also the output shaft ( It is supported by an input disk 28 which limits the axial movement from 12 and is supported by the output shaft 12. That is, the force for maintaining the engaged state is supported by two components, the clutch base 20 and the input disk 28 installed on the output shaft 12. That is, the clutch device 10 is completed as a subassembly of the clutch device 10 that does not require any additional components such as a housing to be provided as a sub-assembly. Therefore, the clutch device 10 can be treated as a single component formed as a subassembly of the output shaft 12.

For example, when an excessive external force (load) of a predetermined value or more is applied to the output shaft 12 through the wiper W, the output shaft 12 is reversed or constrained. Thereafter, the clutch disk 38 rotating together with the output shaft 12 (clutch base 20) causes the clutch disk 38 to rotate relative to the input disk 28 through the clutch base 20. The rotational force is applied in the direction. The sidewalls 34a and 36a of the male engaging portions 34 and 36 of the input disk 28 and the sidewalls 50a and 52a of the female fitting portions 50 and 52 of the clutch disk 38 are inclined (ie, trapezoidal). The clutch base 20 in the axial direction of the output shaft 12 in the clutch disk 38 due to the relative rotational force generated by the relative rotation between the input disk 28 and the clutch disk 38. The component is generated to the side. That is, a part of the relative rotational power generated by the relative rotation between the input disk 28 and the clutch disk 38 is the arm of the numerical coupling parts 34 and 36 of the input disk 28 and the clutch disk 38. The clutch disk 38 is provided as a component for moving the clutch disc 38 in the axial direction of the output shaft 12 to release the engagement between the mating portions 50 and 52. When the relative rotational power (component) becomes equal to or greater than a predetermined value, the clutch disk 38 overcomes the resistance force, and accordingly, the numerical coupling portions 34 and 36 and the clutch disk 38 of the input disk 28 are overcome. The clutch disc 38 is forcibly moved in the axial direction of the output shaft 12 in order to release the engagement between the arm engaging portions 50 and 52 of the arm coupling portion 50, 52. That is, as shown in Figs. 8 and 12, the clutch device 10 is in an uncoupled state, that is, in a declutched state. Therefore, the clutch disk 38, i.e., the output shaft 12, is idle with respect to the input disk 28. As shown in FIG.

Accordingly, damage to each component of the clutch device 10 or each component of the motion converter 94 (components such as the sector gear 132 or the holding lever 138 connected to the input disk 28) is prevented. Or damage to the motor body 92 can be prevented. In addition, the strength of each corresponding component can be set without considering the excessive external force (load) exerted on these components.

Further, in the wiper motor device 90, the clutch base 20 is integrally fixed to the rotational restraint portion 14 of the output shaft 12 having a ridge. In particular, the clutch base 20 is firmly connected to the rotational restraint portion 14 of the output shaft 12 in a rotational direction with respect to the axis of the output shaft 12. The axial movement of the input disk 28 from the output shaft 12 is prevented by the fall prevention portion 16 of the output shaft 12. In addition, the clutch disk 38 is axially movable around the relative rotation shaft portion 18 of the output shaft 12 between the clutch base 20 and the input disk 28. That is, each of the above-described components are installed in the output shaft 12, and the clutch disk 38 is disposed in a predetermined space (predetermined dimension) between the clutch base 20 and the input disk 28. Therefore, as described above, the force (clutch release force, that is, the force for releasing the clutch) required to move the clutch disc 38 in the axial direction can be easily set. Also in this case, as described above, the side walls 34a and 36a of the male engagement portions 34 and 26 of the input disc 28 and the side walls of the female engagement portions 50 and 52 of the clutch disc 38 are described. 50a and 52a are made of an inclined surface, and the clutch release force can be easily set according to the angle of the inclined surface and the resistance force (elastic deformation force) of the wave washer 56.

Further, in the wiper motor device 90, the elastic member is made of a wave washer 56, the resistance applied to the axial movement of the clutch disk 38 is the axial movement of the clutch disk 38. It is satisfied by the resistance of the wave washer 56 is elastically deformed by. Therefore, when an excessive external force (load) is applied to the output shaft 12, the clutch disk 38 withstands the resistance generated by the elastic deformation of the wave washer 56, and thus moves in the axial direction. As a result, the engagement between the clutch disc 38 (female engagement parts 50 and 52) and the input disc 28 (male engagement parts 34 and 36) is released, thereby inputting the clutch disc 38 and the clutch disc 38. Relative rotation occurs between the disks 28.

As described above, when the elastic member is made of the wave washer 56, the force (clutch release force) required to move the clutch disc 38 in the axial direction is stabilized, and as a result, the clutch performance is improved. . In addition, when the elastic member is made of the wave washer 56, the accommodation space for accommodating the elastic member may be made small and thin so that the device can be miniaturized. In addition, unlike the case where the elastic compression deformation rubber material 58 to be described below is used, the wave washer 56 may be damaged by oil such as grease or prevent aging.

Further, in the wiper motor device 90, the wave washer 56 is accommodated in the receiving portion 54 of the clutch device 10, the receiving portion 54 is closed by the clutch base 20. Therefore, the wave washer 56 is disposed around the output shaft 12 without positional deviation with respect to the clutch base 20 and the clutch disc 38. Therefore, the wave washer 56 can impart a stable pressing force (elastic deformation force) to both the clutch base 20 and the clutch disk 38.

In addition, in the wiper motor device 90 of the first embodiment as described above, even when the clutch device 10 is released, the clutch device 10 has the clutch device 10 in its initial position. It can be re-engaged by rotating the motor main body 92 so as to automatically return, so that the output shaft 12 is connected, i.e., coupled to the motor main body 92 at a predetermined point to perform normal operation.

In other words, in the clutch device 10 of the wiper motor device 90 as described above, the respective engagement portions 34 and 36 and the clutch disk 38 of the input disk 28 engaged with each other in a normal operating state. Corresponding engagements of the female engagement portions (50, 52) of the position) are located away from each other. That is, the corresponding engagement portions of the respective engagement portions 34, 36 of the input disc 28 and the female engagement portions 50, 52 of the clutch disc 38 engaged with each other in a normal operating state are clutch devices ( In the clutch release state of 10), they are not engaged with each other in the rotational direction.

Each male engagement portion 34, 36 and one female engagement portion 50, 52 correspond to each other only at a predetermined single point in the normal reciprocation rotation angle range X of the output shaft 12 (wiper W). Are matched. Therefore, when performing the normal operation according to the clutch release of the clutch device 10 as described above, the motor body 92 is rotated again to give the driving force to the input disk 28, and thus the output shaft When the input disk 28 is rotated with respect to 12, each of the male engagement portions 34, 36 and the corresponding female engagement portions 50, 52, which are deviated from each other in the rotational direction, are separated from the output shaft 12. They are again engaged with each other at a predetermined single point in the reciprocating rotation angle range X. That is, each of the male engaging portions 34 and 36 and the corresponding one female engaging portion 50 and 52 are automatically returned to their initial positions so as to be engaged with the clutch device 10.                     

This point will be described with reference to Figs. For simplicity of explanation, FIGS. 14 to 18 show only one male fitting portion 34 and the corresponding female fitting portion 50 among the male fitting portions 34 and 36 and the female fitting portions 50 and 52. Indicated. The following description will also be described correspondingly.

As shown in Fig. 14, when the wiper motor device 10 is stopped at the normal stop position, the wiper W (output shaft 12) is stopped at a predetermined turning position. In addition, the male engagement portion 34 and the female engagement portion 50 mesh with each other, and the male fitting portion 26 of the clutch base 20 is positioned adjacent to the rotation limiting portion 144 of the stopper protrusion 142. (Unmating state).

For example, when the wiper W is forcibly pulled toward the center in the stopped state of the wiper motor device 90, the clutch device 10 is released as shown in FIG. Therefore, while the stop of the input disk 28 is maintained, the clutch base 20 and the clutch disk 38 are forcibly rotated together with the output shaft 12. In other words, the male fitting portion 26 of the clutch base 20 is moved to a position spaced apart from the rotation limiting portion 144 of the stopper protrusion 142, and the female engaging portion 50 is the male fitting portion ( And separated from there).

Here, the clutch device 10 is a clutch release state in which the male engagement portion 34 and the female engagement portion 50 are disengaged from each other, that is, the position of the male engagement portion 34 and the position of the female engagement portion 50. The positions are in the state of Fig. 15 positioned at positions separated from each other in the rotational direction. In this state, when the motor body 92 is rotated again by transmitting a driving force to the input disk 28 to rotate the input disk 28 with respect to the output shaft 12 in order to perform a normal operation. Drag torque of the input disk 28 and the clutch disk 38 (ie, the maximum torque for rotating both the input disk 28 and the clutch disk 38) is output shaft 12 (wiper W). When the load is lower than the load (), the input disk 28 rotates itself as shown in FIG. 16, and the load (load) applied to the output shaft 12 (wiper W). Due to it does not rotate with the clutch disk 38. Thereafter, while the motor body 92 is rotating, the male engaging portion 34 and the female engaging portion 50 mesh with each other at a predetermined single point in the normal reciprocating rotational angle range X of the output shaft 12. As a result, normal operation is resumed.

On the other hand, the clutch disengagement state of the clutch device 10 in which the male engagement portion 34 and the female engagement portion 50 disengage from each other, that is, the male engagement portion 34 and the female engagement portion 50 is shown in FIG. As shown in FIG. 2, the motor body 92 is transmitted by transmitting a driving force to the input disk 28 to rotate the input disk 28 with respect to the output shaft 12 so as to perform a normal operation in the clutch release state moved from each other in the rotational direction. ), The drag torque of the input disk 28 and the clutch disk 38 (that is, the maximum torque for rotating both the input disk 28 and the clutch disk 38) is outputted. When larger than the load (load) applied to the shaft 12 (wiper W), the input disk 28 is rotated together with the clutch disk 38 as shown in FIG. In other words, the clutch disk 38 is engaged with the input disk 28 at a reduced rotational coupling force less than the maximum rotational coupling force such that when the input disk 28 is rotated, it rotates along the input disk 28. In this manner, while the input disk 28 rotates together with the clutch disk 38, the male fitting portion 26 of the clutch base 20 contacts the other rotation limiting portion 146 of the stopper protrusion 142. Thus, the rotation of the clutch disc 38 is limited. At this time, the rotation of the wiper (W) is limited to within a predetermined limit angle range Y. Therefore, the wiper W does not move to the vehicle body area exceeding the window glass area of the vehicle, so that the wiper W does not damage the vehicle body.

Then, the input disk 28 is further rotated with respect to the clutch disk 38, which is limited in further rotation. Then, as shown in Fig. 18, the male engagement portion 34 and the female engagement portion 50 are again engaged with each other at a predetermined single point of the normal reciprocation rotation angle range X of the output shaft 12. Therefore, normal operation is resumed.

As described above, in the wiper motor device 10 (clutch device 10) of the present embodiment, the clutch device 10 is de-clutched, that is, the output shaft 12 (wiper W) and the motor main body 92 In a state in which relative rotation occurs between the), when the motor body 92 further rotates, the clutch device 10 is automatically returned to its initial position, and the motor body 92 side has an output shaft 12 ) That is, the clutch device 10 is engaged at a predetermined point to resume normal operation.

In addition, in the wiper motor device 90, two pairs of male engagement portions 34 and 36 and two pairs of female engagement portions 50 and 52 are provided. Therefore, the drive torque transmitted from the input disk 28 (the male engaging portions 34 and 36) to the clutch disk 38 (the female engaging portions 50 and 52) has a large torque and the output shaft 12 It can be increased to drive. Therefore, the motor device 90 can be effectively used as a driving source of a vehicle wiper system or sunroof system.

Further, in the wiper motor device 90 (clutch device 100), the rotation limit unit 144, 146 for limiting the reciprocating rotation of the clutch disk 38 (clutch base 20 and output shaft 12). ) May be integrally formed with the stopper protrusion 142 provided in the housing 96 rotatably supporting the output shaft 12. Therefore, the stopper protrusion 142 may be integrally formed with the housing 96. As a result, the accuracy of the limiting angle of the stopper protrusion 142 (limiting angle range Y of the rotation limiting portions 144 and 146) is improved, and the configuration is simplified.

In addition, the male fitting portion 26 engaged with the stopper protrusion 142 is formed to protrude radially outward of the clutch disk 38 and the clutch base 20. In other words, the components which limit the reciprocation of the clutch disc 38 (clutch base 20 and output shaft 12) are located at positions as far as possible radially away from the output shaft 12. As shown in FIG. Therefore, the accuracy of the limit angle formed by the stopper protrusion 142 and the male fitting portion 26 (limit angle range Y of the rotation limiting portions 144 and 146) is further improved.

Further, in the wiper motor device 90 (clutch device 10) of the first embodiment, between the output shaft 12 (rotary restraint portion 14) and the clutch base 20 (support hole 22). The fixed strength in the rotational direction is set larger than the connection strength of the wiper W in the rotational direction of the output shaft 12. Therefore, for example, in the clutch release state of the clutch device 10, the rotation of the output shaft 12 (wiper W) is limited by the rotation limiting part of one of the rotation limiting parts 144, 146. In the state, when an excessive load is further applied to the wiper W to rotate the output shaft 12 beyond the limit angle range Y, the wiper W is output shaft 12 (rotational restraint 14 Rotated relative to)). Thus, excessive load is not transmitted to the internal components of the motor device 90. Therefore, the driving force transmission components positioned next to the output shaft 12 can be protected. These components are, for example, components of the clutch device 10, components of the motion converter 94 (for example, the sector gear 132 and the retaining lever 138 connected to the input disk 28). ), And components such as a worm wheel 128, a worm gear 122, and a motor body 92 positioned between the output shaft 12 and the armature 108.

As described above, in the wiper motor device 90 (clutch device 10) of the present embodiment, the clutch device 10 is in a clutch released state, that is, the output shaft 12 (wiper W) and the motor main body ( 92)) in the state where relative rotation occurs, when the motor body 92 is further rotated, the clutch device 10 is automatically returned to its initial position, and the motor body 92 is output shaft ( 12). That is, the clutch device 10 is engaged at a predetermined point to resume normal operation. In addition, damage to the components or damage to the drive-side components (for example, damage to the motor body 92) can be prevented when locking the output shaft 12 (wiper W).

Thus, the wiper motor device 90 is exaggerated to the output shaft 12 through the wiper W when applied to the wiper arm, for example, as a large amount of snow accumulated on the roof of the vehicle falls vertically along the window pane surface. It is suitable as a wiper motor of a vehicle such as a truck or a construction machine with a high probability cap-over type cockpit to which a force (load) is to be applied.

In the first embodiment, the wave washer 56 is used as the elastic member of the clutch device 10. However, the elastic member of the clutch device 10 is not limited to the wave washer 56.

For example, as in the case of the clutch device 11 shown in Fig. 19, a rubber member 58 in the form of a circular disk can be used as the elastic member. The resistance applied to the clutch disk 38 to limit the axial movement of the clutch disk 38 may be implemented by the restoring force of the rubber member 58 which is elastically deformed. When the rubber member 58 is used as the elastic member, the clutch disk 38 (female engagement portions 50 and 52) and the input disk 28 (numbering portions 34 and 36) during normal operation. It is possible to avoid applying a pressing force for maintaining the teeth between the teeth. Therefore, for example, the influence of the long time stress accompanied by the deformation of the elastic member can be reduced, so that the aging of the elastic member is prevented.

In addition, the elastic member is not limited to the wave washer 56 or the rubber member 58, a compression coil spring or a belleville spring (belleville spring) may be used.

Also, in this case, when the normal state (the clutch disc 38 is not moved toward the clutch base 20 side), each elastic member such as the rubber member 58 is the clutch base 20 and the clutch disc ( 38) A pressing force can be applied between. In addition, each of the elastic members such as the rubber member 58, only when the clutch disk 38 is moved to the clutch base 20 side, that is, the male engagement portion 34, 36 is female engagement portion (50, 52) The pressing force may be applied to the clutch disc 38 only when the vehicle is to move away from the clutch disc 38.

Next, other embodiments of the present invention will be described. Components similar to those of the first embodiment are denoted by the same reference numerals throughout the other embodiments, and detailed description thereof will be omitted.

(Second Embodiment)

20 is an exploded perspective view showing the clutch device 60 according to the second embodiment of the present invention.

The clutch device 60 basically has the same configuration as that of the clutch device 10 of the first embodiment. However, the clutch device 60 includes another clutch base 62 instead of the clutch base 20 in the first embodiment, and another clutch disk (instead of the clutch disk 38 in the first embodiment). Second rotating member) 64.

The clutch base 62 is formed in a cup shape and includes a base wall 68 and a peripheral wall 70. The base wall 68 has a support hole 66 corresponding to the output shaft 12 and penetrating the base wall 68. The peripheral wall 70 extends in the axial direction of the output shaft 12 from the peripheral edge of the base wall 68. The support hole 66 is fixed to the rotational restraint portion 14 of the output shaft 12, and the clutch base 62 is integrally rotated with the output shaft 12. Female fitting guide portions 72 and 74 are provided at the open side peripheral portion of the peripheral wall 70.

The clutch disk 64 is formed in a circular disk-shaped body and has a shaft hole 76 corresponding to the output shaft 12. The output shaft 12 (relative rotation shaft portion 18) is received through the shaft hole 76 of the clutch disk (64). The clutch disk 64 is located on the other shaft end side (clutch base 62 side) of the output shaft 12 with respect to the input disk 28, and the clutch disk 64 is mounted with respect to the output shaft 12. The output shaft 12 is supported by the output shaft 12 in such a manner as to be movable in the axial direction of the output shaft 12. In addition, the outer peripheral portion of the clutch disk 64 is provided with a pair of male fitting portions 78 and 80 corresponding to the female fitting guide portions 72 and 74 of the clutch base 62. The male fitting portions 78 and 80 are located opposite to each other in the peripheral direction of the clutch disk 64, and protrude in the radial direction of the output shaft 12. That is, the male fitting portions 78 and 80 are positioned at positions 180 degrees apart from each other in the peripheral direction of the clutch disk 64 and protrude in the radial direction of the output shaft 12. The male fitting portions 78 and 80 of the clutch disk 64 are moved in the axial direction and are fitted to the female fitting guide portions 72 and 74 of the clutch base 62. Accordingly, the clutch disk 64 is rotated together with the clutch base 62 (that is, the output shaft 12), and axially movable in the axial direction of the output shaft 12 with respect to the clutch base 62. do.

In addition, similarly to the first embodiment, two pairs of female engaging portions 50 and 52 are formed on the rear surface of the clutch disk 64 (the input disk 28 side, that is, one shaft end side of the output shaft 12). Is formed in a groove shape.

In addition, the inner space formed by the inner side of the clutch base 62, that is, the base wall 68 and the peripheral wall 70 forms a receiving portion 82. The clutch disk 64 is fitted to the open side peripheral portion of the peripheral wall 70 of the clutch base 62 in such a way that the clutch disk 64 closes the receiving portion 82.

The accommodating part 82 accommodates the rubber member 84 provided as an elastic member. The rubber member 84 is disposed between the clutch base 62 (base wall 68) and the clutch disk 64. The rubber member 84 is a state in which the male engaging portion 34 of the input disk 28 and the female engaging portion 50 of the clutch disk 28 are engaged with each other with respect to the axial movement of the clutch disk 64. To the other shaft end side (clutch base 62 side) of the output shaft 12 from the predetermined pressing force (the rubber member 84 generated by the axial movement of the clutch disc 64) is elastically deformed. Acting resilience).

The other components of the second embodiment are the same as those of the clutch device 10 of the first embodiment.

In the first embodiment, the clutch device 10 is applied to the wiper motor device 90. However, the present invention is not limited thereto. For example, the wiper motor can be formed by using the clutch device 60 of the first embodiment.

In this case, the protrusion 71 engaged with the rotation limiting portion 144 or 146 of the stopper protrusion 142 may be formed on the peripheral wall 70 of the clutch base 62. Accordingly, the rotation of the clutch base 62 (output shaft 12) can be limited within a predetermined range.

Next, the operation of the second embodiment will be described.

The clutch device 60 (and the wiper motor device including the clutch device 60) provides an effect similar to that of the clutch device 10 and the wiper motor device 90 of the first embodiment.                     

More specifically, in the normal operation state, when a driving force is provided to the input disk 28 to rotate the input disk 28 with respect to the output shaft 12, the rotation driving force is the numerical engagement portion 34, 36 and the female engagement portion 50, 52 is transmitted from the input disk 28 to the clutch disk 38. Since the clutch disc 64 meshes with the clutch base 62 fixed to the output shaft 12, the rotational driving force transmitted to the clutch disc 64 is transmitted from the clutch disc 64 to the clutch base 62. do. Therefore, the output shaft 12 is rotated together with the clutch disk 64 and the clutch base 62.

Here, even in the case of the clutch device 60, when the rotation driving force is transmitted from the input disk 28 to the output shaft 12 in the normal operation state (rotation state) as described above, the rotation driving force Can be transmitted without generating sliding motion in any of the components involved. More specifically, the engagement between the male engagement portions 34 and 36 of the input disc 28 and the female engagement portions 50 and 52 of the clutch disc 38 is maintained from the engagement state of the clutch disc 64. The resistance of the rubber member 84 applied to the clutch disc 64 is not consumed by sliding friction. Therefore, the fall of rotation transfer efficiency can be prevented. Further, since the rotational driving force can be transmitted without generating any sliding motion in the related components, noise generation that can be generated by the sliding movement of the related components can be prevented.

As described above, the engagement state between the male engagement portions 34 and 36 of the input disc 28 and the female engagement portions 50 and 52 of the clutch disc 38 is determined from the engagement state of the clutch disc 64. The resistance force of the rubber member 84 applied to the clutch disk 64 to hold is received by the clutch base 62 fixed to the output shaft 12, and is also supported by the input shaft 12 28, the axial movement of the input disc 28 from the output shaft 12 is prevented. That is, the force for maintaining the engagement state is supported by two components, the clutch base 62 and the input disk 28 provided on the output shaft 12. In other words, the clutch device 60 is completed as a subassembly of the output shaft 12 that does not require any additional components, such as a housing, to serve as a sub-assembly. Therefore, the clutch device 60 can be treated as a single component formed as a subassembly of the output shaft 12.

For example, when an excessive external force (load) is applied to the output shaft 12, the output shaft 12 is reversed or constrained. Thereafter, the clutch disk 64 that rotates together with the output shaft 12 (clutch base 62) rotates through the clutch base 62 to rotate the clutch disk 64 with respect to the input disk 28. This is working. The sidewalls 34a and 36a of the male engaging portions 34 and 36 of the input disk 28 and the sidewalls 50a and 52a of the female fitting portions 50 and 52 of the clutch disk 64 are inclined (ie, trapezoidal). Cross section), the clutch disc 64 in the axial direction of the output shaft 12 in the clutch disc 64 due to the relative rotational force generated by the relative rotation between the input disc 28 and the clutch disc 64. 20) The component is generated to the side. When the relative rotational power (component) is equal to or greater than a predetermined value, the clutch disk 64 is forced to move in the axial direction of the output shaft 12 to withstand the resistance applied from the rubber member 84 and release the engagement. (Ie, the male engagement portions 34 and 36 are moved away from the female engagement portions 50 and 52 of the clutch disc 64). Therefore, relative rotation occurs between the clutch disk 64, that is, the output shaft 12 and the input disk 28.

Accordingly, damage to each component connected to the input disk 28 or damage to the motor main body 92 can be prevented. In addition, the strength of each corresponding component can be set without considering the excessive external force (load) applied to these components.

Further, even when the clutch device 60 of the second embodiment is in the clutch release state, the clutch device 60 (and the wiper motor device including the clutch device 60) is operated normally by the rotation of the motor body 92. It may be automatically returned to the initial position to connect the output shaft 12 (wiper W) to the motor main body 92 at a predetermined point to resume the operation.

That is, in the clutch device 60 as described above, the respective female engagement portions 34 and 36 of the input disc 28 and the corresponding female engagement portions of the clutch disc 64 engage each other in a normal operating state. 50 and 52 are located at positions away from each other. That is, each male engaging portion 34, 36 of the input disk 28 and the corresponding female engaging portion 50, 52 of the clutch disk 64 engaged with each other in a normal operating state are the clutch device 60. Are engaged with each other in the rotational direction in the clutch release state. Each of the male engagement portions 34 and 36 and the corresponding female engagement portions 50 and 52 correspond to each other only at a predetermined single point within the normal reciprocation rotation angle range X of the output shaft 12 (wiper W). Are matched. Therefore, as described above, when the clutch device 60 performs the normal operation as the clutch device is released, the driving force is provided to the input disk 28, and thus the input disk 28 to the output shaft 12. When the motor body 92 is rotated again to rotate), each of the numerical coupling parts 34 and 36 and the corresponding female coupling parts 50 and 52 which are moved to each other in the rotational direction are connected to the output shaft. They are meshed again with each other at a predetermined single point within the normal reciprocating rotation angle range X of (12). That is, each of the male engaging portions 34 and 36 and the female engaging portions 50 and 52 are automatically returned to their initial positions to engage the clutch device 60.

As described above, even when the clutch device 60 of the second embodiment is released, that is, even when a relative rotation occurs between the output shaft 12 (wiper W) and the motor body 92, the clutch device. (60) (and the wiper motor device including the clutch device 60) the output shaft 12 (wiper W) at a predetermined point to resume normal operation through the rotation of the motor body 92. It automatically returns to its initial position for connection to the motor body 92.

In addition, the protrusions 71 engaged with the rotation limiting portions 144 and 146 of the stopper protrusion 142 are formed on the peripheral wall 70 of the clutch base 62. That is, the components for limiting the reciprocating rotation of the clutch disc 64 (clutch base 62 and output shaft 12) are located at a position as far as possible in the radial direction from the output shaft 12. Therefore, the accuracy of the limit angles (limit angle ranges Y of the rotation limiting portions 144 and 146) formed by the stopper protrusion 142 and the protrusion 71 is further improved.

As described above, the clutch device 60 (and the wiper motor device with the clutch device 60) according to the second embodiment is the unit of the wiper motor device 90 (the clutch device 10) of the first embodiment. It has an effect similar to that of the effect. When the output shaft 12 is locked, it is possible to prevent damage to corresponding components and breakage of the motor body 92, respectively. Further, even when a relative rotation occurs between the output shaft 12 (driven component) and the motor body 92 (drive side component), that is, even when the clutch device 60 is released, The clutch device 60 includes a motor main body 92 for reconnecting the output shaft 12 (drive side component) to the motor body 92 (drive side component) at a predetermined point to resume normal operation. It is automatically returned to its initial position through the rotation of the drive side component).

(Third Embodiment)

21 is a sectional view showing the motor device 150 according to the third embodiment of the present invention.

The motor device 150 basically has the same configuration as that of the wiper motor device 90 of the first embodiment. The motor device 150 includes a motor body 92, a motion converter 152 and a clutch device 154.

The motor body 92 has a configuration substantially the same as that of the motor body 92 of the first embodiment. In the first embodiment, the motor body 92 (an armature 108) is rotated in one direction. In contrast, the motor body 92 in the third embodiment is rotated in the normal direction and the reverse direction between the rotation limiting portions 144, 146 of the stopper protrusion 142.

In the motion converter 152, the sector gear 132 and the holding lever 138 of the first embodiment are omitted. Therefore, the motion converter 152 includes a worm gear 122 and a worm wheel 128.                     

In addition, the worm wheel 128 is provided as an input disk of the clutch device 154. That is, the worm wheel 128 functions as an input disk (or first rotating member) of the clutch device 154. In other words, the clutch device 154 basically has the same configuration as that of the clutch device 10 of the first embodiment. However, the clutch device 154 is configured in such a manner that the input disk 28 of the first embodiment is provided with worm teeth engaged with the worm gear 122.

In such a motor device 150, when the motor body 92 (an armature 108) is rotated, the rotational force is transmitted to the worm wheel 128 through the worm gear 122 to rotate the worm wheel 122.

Here, the worm wheel 128 is provided as an input disk (or first rotating member) of the clutch device 154. That is, the worm wheel 128 functions as an input disk of the clutch device 154. Therefore, in the normal operation as described in the first embodiment, the output shaft 12 is integrally rotated with the worm wheel 128.

Even in the case of such a motor device 150, when transmitting the rotational driving force to the clutch device 154 in a normal operating state (rotational state), the rotational driving force can be transmitted without generating any sliding movement of the related components. Therefore, the decrease in rotational transfer efficiency can be prevented. In addition, since the rotational driving force can be transmitted without the occurrence of any sliding movement of the related components, noise generation that can be generated by the sliding movement of the related components can be effectively prevented.

For example, when an excessive external force (load) is applied to the output shaft 12, the output shaft 12 is rotated or constrained in the reverse direction. Thereafter, as described in the first embodiment, relative rotation occurs between the output shaft 12 and the worm wheel 128. Accordingly, it is possible to prevent damage to each component of the clutch device 154, damage to components of the motion conversion apparatus 122 such as the worm gear 122 connected to the worm wheel 128, and damage to the motor body 92. Can be. In addition, the strength of each corresponding component can be set without considering the excessive external force (load) applied to these components.

Further, even in the case of the motor device 150 of the third embodiment, similarly to the first embodiment, the clutch device 154 is in the disengaged state, that is, the relative rotation between the output shaft 12 and the motor body 92. In this state, the clutch device 154 automatically rotates the motor body 92 to its initial position by reconnecting the output shaft 12 to the motor body 92 to resume normal operation. Can be reset.

In addition, the rotation of the worm wheel 128 (the input disk of the clutch device 154) is decelerated through engagement with the worm gear 122 provided on the rotation shaft 110 of the motor body 92. Therefore, the input shaft 12 can be driven with a relatively large torque. Therefore, the motor device is suitable as a drive source of the wiper system or the sunroof system.

(Fourth Embodiment)

Fig. 22 is a sectional view showing the wiper motor device 290 having the clutch device 210 according to the fourth embodiment of the present invention.

The wiper motor device 290 is similar to the configuration of the wiper motor device 90 of the first embodiment, and has a configuration including a clutch device 210.

As shown in Figs. 23 and 24, the output shaft 12 to which the clutch device 210 is provided has a cylindrical portion having a circular cross section at the front end side (the upper side in Figs. 23 and 24) of the output shaft 12. As shown in Figs. (213). The base end side (lower side in Figs. 23 and 24) of the output shaft 12 includes a relative rotation limiting portion 214. The relative rotation limiting portion 214 is formed between a substantially rectangular cross section (double D-cut cross sectional shape) having two flat surfaces moved to each other by 180 degrees in the circumferential direction and the flat surface. Cross section consisting of two arches).

As shown in FIG. 22, the cylindrical portion 213 of the output shaft 12 is rotatably supported by a bearing member 250 fixed to the housing 96. An axial protrusion 216a is formed on the arcuate surface of the tip side (cylindrical portion 213 side) of the relative rotation limiting portion 214 to form the rotational restriction portion 216. The fall prevention part 218 is formed at the base end of the relative rotation limiting part 214.

Engaging base (base member) 220 provided as a large diameter portion having a large diameter in the radial direction of the output shaft 12 is coaxial with respect to the output shaft 12, For example, it is fixed to the rotation restraint part 216 of the relative rotation limiting part 214 by press fitting. That is, the coupling base 220 has the output shaft in such a manner that the coupling base 220 is not axially movable with respect to the output shaft 12 and cannot be rotated with respect to the output shaft 12. Supported by (12). The coupling base portion 220 is formed of a circular disk-shaped body, and has a support hole 222 in the center thereof. The support hole 222 has a substantially rectangular cross section (double D-shaped cross section) corresponding to the relative rotation limiting portion 215 of the output shaft 12. When the support hole 222 is fixedly connected to the relative rotation limiting portion 216, the coupling base portion 220 is rotated together with the output shaft 12, with respect to the output shaft 12 in the axial direction. It is fixed. In addition, a stopper portion 226 is formed on the outer circumference of the coupling base portion 220, and the stopper portion 226 protrudes in a radial direction (radial direction of the output shaft 12). The stopper part 226 corresponds to the stopper protrusion 142 formed in the housing 96.

The configuration is not limited to a configuration in which the output shaft 12 and the coupling base portion 220 are formed separately and then fixedly connected to each other. For example, another configuration in which the output shaft 12 and the coupling base portion 220 are integrally formed through, for example, a cold forging process (a configuration in which a flange such as a large diameter portion is integrally formed in the output shaft). It may be provided as.

The gear member 228 provided as an input disk (or first rotating member) is provided in the fall prevention portion 218 of the relative rotation limiting portion 214 in a coaxial relationship with respect to the output shaft 12. The gear member 228 is formed of a cylindrical body and has a circular shaft hole 230 at the center of the gear member 228. The fall prevention part 218 of the output shaft 12 is accommodated through the shaft hole 230, and a clip 32 is installed in the fall prevention part 218. Therefore, the gear member 228 can not be separated from the output shaft 12 in the axial direction of the output shaft 12, the gear member 228, the relative rotation limiting portion 214 of the output shaft 12 In such a way as to be rotatable with respect to, the output shaft 12 is supported by one side shaft end side (the side opposite from the coupling base 220). Therefore, in this case, the relative rotation limiting portion 214 of the output shaft 12 in which the gear member 228 is installed is rotated relative to the output shaft 12 like the relative rotation shaft 18 of the first embodiment. It is provided as a shaft portion. In the fourth embodiment, the gear member 228 is a sintered metal product formed by a power metallurgy process in the following manner. In other words, the powder alloy is first filled in a mold unit, and then the powder alloy is molded and sintered in the mold unit by compression molding. The sintered metal product includes lubricating oil.

A gear tooth 234 is formed at an outer circumferential portion of one shaft end portion of the gear member 228 disposed to face the coupling base portion 220. The gear tooth 234 meshes with the tooth forming portion 136 of the sector gear 132 of the swing device 94. When a driving force is transmitted from the sector gear 132, the gear member 228 is rotated relative to the output shaft 12.

In addition, as shown in Fig. 24, the other end of the gear side 234 (coupling base portion 220 side facing away from the holding lever 138) so that the shaft end of the gear tooth 234 is connected together. The connection member 228 is formed on the gear member 228. The connecting wall 235 and the holding lever 138 hold the gear tooth forming portion 136 of the sector gear 132 in the thickness direction of the gear tooth forming portion 136 of the sector gear 132. In other words, the connecting wall 235 is positioned opposite to one end surface of the tooth forming portion 136 in the thickness direction, and the retaining lever 138 is opposite to the other end surface of the cheer forming portion 136 in the thickness direction. Is located. Therefore, the movement of the sector gear 132 in the thickness direction is limited.

In addition, a cylindrical peripheral surface 236 coaxial with the output shaft 12 is formed on the outer circumferential portion of the gear member 228 positioned opposite from the gear tooth 234 with respect to the connecting wall 235. The cylindrical peripheral surface 236 is rotatably supported by a bearing member 252 fixed to the housing 96. In other words, at the other shaft end side of the gear tooth 234, the gear member 228 has a cylindrical disk-shaped flange coaxial with the output shaft 12, the outer peripheral surface (cylindrical peripheral surface 236) ) Is supported by the bearing member 252.

In addition, at the outer periphery of the cross section of the gear member 228 located on the other shaft end side (coupling base 220 side, that is, on the other shaft end side of the output shaft 12), four engagement protrusions (numeric engagement parts or The first side engagement portion 237 protrudes toward the coupling base portion 220. The engagement protrusions 237 are disposed in a coaxial relationship with respect to the gear member 228, and are arranged at different intervals (each of which is different from an adjacent interval) in the circumferential direction of the gear member 228. The fitting protrusion 237 corresponds to a fitting groove (female fitting part or second side fitting part) 242 of the coupling plate 238 to be described later.

The engaging plate 238, which is provided as a clutch disk (or second rotating member), is provided between the engaging base portion 220 and the gear member 228 such that the engaging plate 238 is coaxial with the output shaft 12. Is supported by the relative rotation limiting portion 214 of the output shaft 12. The coupling plate 238 is formed of a circular disk and has a shaft hole 240 in the center thereof. The shaft hole 240 has a substantially rectangular cross section (double D-shaped cutting cross section) corresponding to the relative rotation limiting portion 214. When the shaft hole 240 receives the output shaft 12 (relative rotation limiting portion 214), the coupling plate 238 is the other shaft end portion of the output shaft 12 with respect to the gear member 228 It is located in the side (coupling base part 220 side). The coupling plate 238 is driven by the output shaft 12 in such a way that the coupling plate 238 is not rotatable with respect to the output shaft 12 and axially movable with respect to the output shaft 12. Supported. Therefore, the coupling plate 238 is integrally rotated with the output shaft 12 and relatively movable in the axial direction of the output shaft 12. In the fourth embodiment, the coupling plate 238 is formed through the above-described powder metallurgy process and is made of a sintered metal product including lubricating oil.

The four engagement grooves 242 are formed in a groove shape on the outer circumferential portion (the gear member 228 side, that is, one shaft end side of the output shaft 12) of the rear surface of the coupling plate 238. The engagement groove 242 corresponds to four engagement protrusions 237 of the gear member 228. In addition, the engagement grooves 242 are arranged in a coaxial relationship with respect to the coupling plate 238, and are arranged at different intervals (each interval adjacent to each other) in the peripheral direction of the coupling plate 238.

The four engagement grooves 242 may engage with four engagement protrusions 237 of the gear member 228, respectively. That is, the coupling plate 238 is meshable with the gear member 228. Therefore, in the normal operation state (rotation state), when the gear member 228 is rotated, the rotational force of the gear member 228 is transmitted to the coupling plate 238. Therefore, the coupling plate 238 is rotated together with the gear member 228.

However, as described above, the engaging protrusion 237 and the toothing groove 242 are arranged at different intervals (each different interval from each other adjacent) in the peripheral direction of the gear member 228 and the coupling plate 238. . Therefore, the coupling plate 238 (output shaft 12 and wiper) and gear member 228 mesh with each other only at a predetermined single peripheral point. In other words, at a peripheral direction point other than a predetermined single peripheral direction point, even if one of the engagement protrusions 237 coincides with one of the engagement grooves 242, that is, one of the engagement protrusions 237 is the engagement groove. Even when aligned with one of 242, the other three engagement protrusions 237 are not aligned with the other three engagement grooves 242. Therefore, when the engagement protrusion 237 is moved from the engagement groove 242, the coupling plate 238 is contacted through at least three engagement protrusions 237 (providing three support points).

In addition, the side wall 237a of the fitting protrusion 237 of the gear member 228 and the side wall 242a of the fitting groove 242 of the coupling plate 238 have an inclined surface. In other words, each engagement protrusion 237 of the gear member 228 has a trapezoidal cross section, and each engagement groove 242 of the coupling plate 238 has a corresponding trapezoidal cross section. Accordingly, when the gear member 228 rotates, the rotational force is transmitted from the gear member 228 to the coupling plate 238, so that the coupling plate 238 is engaged in the axial direction of the output shaft 12. The component force is generated toward the base portion 220.

Both the side wall 237a of the engaging protrusion 237 of the gear member 228 and the side wall 242a of the engaging groove 242 of the coupling plate 238 need not have the inclined surface as described above. For example, only one of the side walls 237a of each of the engagement protrusions 237 of the gear member 228 may be formed of an inclined surface inclined in the peripheral direction or inclined in the peripheral direction. In addition, only one of the sidewalls 242a of each of the engaging grooves 242 of the coupling plate 238 may be formed of an inclined surface inclined in the peripheral direction or inclined with respect to the peripheral direction. Even with this configuration, the component force may be generated in the coupling plate 238 in the axial direction of the output shaft 12 by the transmission of the rotational force from the gear member 228 to the coupling plate 238.

In addition, a compression coil spring 244 is disposed between the coupling plate 238 and the coupling base portion 220. The coil spring 244 is elastically wound around the output shaft 12 and is compressively provided in the axial direction of the output shaft 12. The coil spring 244 is the other shaft end side of the output shaft 12 from the state in which the engagement protrusion 237 of the gear member 228 and the engagement groove 242 of the coupling plate 238 are engaged with each other ( The elastic force generated by the elastic deformation of the coil spring 244 through the axial movement of the coupling plate 238 with respect to the axial movement of the coupling plate 238 toward the coupling base portion 220 side. Given restoring force).

In other words, the engagement protrusion 237 of the gear member 228 is generally engaged with, or received, the engagement groove 242 of the coupling plate 238, and the coil spring 244 maintains this engagement state. When the engagement protrusion 237 of the gear member 228 is moved away from the engagement groove 242 of the coupling plate 238, the coupling plate 238 tries to axially move toward the coupling base portion 220 side. . The coil spring 244 provides resistance (restoration force) to this axial movement of the coupling plate 238.                     

In addition, as described above, when the engaging projection 237 of the gear member 228 is accommodated in the engaging groove 242 of the coupling plate 238, that is, the engaging projection 237 of the gear member 228 is When engaged with the engaging groove 242 of the coupling plate 238, the rotational force is transmitted from the gear member 228 to the coupling plate 238. However, even when the engaging projection 237 of the gear member 228 is disengaged from the engaging groove 242 of the engaging plate 238, that is, the engaging plate 238 is moved to the engaging base portion 220 side. Even in this case, a predetermined frictional force is generated between the engagement protrusion 237 of the gear member 228 and the rear surface of the coupling plate 238 due to the pressing force of the coil spring 244. Therefore, the coupling plate 238 is rotated together with the gear member 228 due to the friction force of the coil spring 244. The pressing force of the coil spring 244 is set to achieve such rotation of the coupling plate 238 together with the gear member 228 even in a decoupled state.

In the normal state, that is, when the coupling plate 238 does not move toward the coupling base portion 220, the coil spring 244 always applies an appropriate pressing force to the coupling base portion 220 and the coupling plate 238. Can be. In addition, the coil spring 244 is only when the coupling plate 238 tries to move toward the coupling base portion 220, that is, when the engagement protrusion 237 tries to disengage from the engagement groove 242. , More pressing force (restoration force) can be applied.

As shown in FIG. 22, the above-mentioned stopper protrusion 142 is formed in the housing 96 so as to correspond to the stopper portion 226 of the engaging base portion 220. As shown in FIG.

The stopper protrusion 142 is formed in an arcuate body and is positioned in the rotation path of the stopper part 226 to which the stopper part 226 moves while the coupling base part 220 rotates. The first rotational limiting portion 144 is formed at one side peripheral end of the stopper protrusion 142, and the second rotational limiting portion 146 is formed at the other main peripheral end of the stopper protrusion 142. In other words, each of the rotation limiting portions 144 and 146 of the stopper protrusion 142 may be engaged with the respective stopper portions 226. When the stopper part 226 is engaged with the first rotation limiting part 144 or the second rotation limiting part 146 of the stopper protrusion 142, the coupling base part 220 (the output shaft 12) Further rotation is limited. Therefore, by acting the rotational driving force of the gear member 228 to the engaging base portion 220 (output shaft 12), together with the engaging plate 238 the engaging base portion 220 (output shaft 12) ), When the stopper part 226 is engaged with the first rotation limiting part 144 or the second rotation limiting part 146 of the stopper protrusion 146, the coupling base part 220 (output Further rotation of the shaft 12 is forcibly limited. Therefore, relative rotation is generated between the gear member 228 and the engaging base portion 220 (output shaft 12).

The wiper (not shown) may be directly connected to the output shaft 12 reciprocating by the gear member 228. In addition, the wiper (not shown) may be indirectly connected to the output shaft 12 through a link or a rod. Therefore, the wiper swings reciprocally by reciprocating rotation of the output shaft 12.

Next, the operation of the fourth embodiment of the present invention will be described.

In the wiper motor device 9, when the motor body 92 (the armature 108 rotates), the rotational force is transmitted to the worm wheel 128 through the worm gear 122 to rotate the worm wheel 128. The worm wheel When the 128 rotates, the sector gear 132 connected to the worm wheel 128 swings reciprocally. Then, the reciprocating swing movement of the sector gear 132 reciprocates the gear member 228.

In a normal operating state, the engaging projection 237 of the gear member 228 is engaged with the engaging groove 242 of the coupling plate 238. In addition, even when the coupling plate 238 tries to move in the axial direction of the output shaft 12 from the engaged state in which the engaging protrusion 237 is engaged with the engaging groove 242, a predetermined resistance force is obtained by the coil spring ( 244 is applied to the coupling plate 238. Therefore, the engagement state is maintained. In addition, the coupling plate 238 cannot be rotated about the axis of the output shaft 12. Therefore, when the gear member 228 reciprocates, the rotational driving force is transmitted from the gear member 228 to the coupling plate 238 through the engaging protrusion 237 and the engaging groove 242. Thus, the output shaft 12 is integrally rotated with the coupling plate 238.

Accordingly, the wiper connected to the output shaft 12 is reciprocated in accordance with the reciprocating rotation of the output shaft 12.

For example, when an excessive external force (load) is acted on the output shaft 12 through the wiper, the output shaft 12 is reversed or constrained. Thereafter, the coupling plate 238 rotated together with the output shaft 12 receives a rotational force in a direction causing rotation of the coupling plate 238 with respect to the gear member 228. Since the side wall 237a of the engagement protrusion 237 of the gear member 228 and the side wall 242a of the engagement groove 242 of the coupling plate 238 have an inclined surface (that is, a trapezoidal cross section), the coupling plate In 238, the component force is generated toward the coupling base 220 in the axial direction of the shaft output 12 due to the relative rotational force generated by the relative rotation between the gear member 228 and the coupling plate 238. In other words, a part of the relative rotational power generated by the relative rotation between the gear member 228 and the coupling plate 238 is the engaging groove 237 of the engagement protrusion 237 and the coupling plate 238 of the gear member 228. 242 is provided as a component to move the coupling plate 238 in the axial direction of the output shaft 12 to release the engagement between. When the relative rotational power (calorie) is equal to or greater than a predetermined value, the coupling plate 238 overcomes the resistance of the coil spring 244, and thus the engagement protrusion 237 and the coupling plate of the gear member 228. It is forcibly moved in the axial direction of the output shaft 12 to release the engagement between the engagement grooves 242 of (238). Accordingly, the coupling plate 238, that is, the output shaft 12 is rotated relative to the gear member 228.

Therefore, the wiper is frozen on the wiping window surface at the normal stop position in the rotation angle range, or in a state in which a large amount of snow is laid on the wiper held at the normal stop position and the wiper is constrained. When the motor main body 92 of the wiper motor device 290 is rotated and an excessive load or a sudden load is applied, the clutch device 210 is released from the clutch. Further, while the wiper is operated within the rotation angle range (normal wiping range) of the wiper, the wiper is positioned on the roof of the vehicle at a position other than the lower reversal point when the wiper is wiped. When excessive amount of external force is applied to the output shaft 12 through the wiper, such as when a large amount of snow falls along the window surface, the clutch device 120 is released. Accordingly, driving force transmission components other than the gear member 228 (sector gear 132, worm wheel 128, worm gear 122 and the motor body (120) disposed between the output shaft 12 and the armature 108) 92) can prevent excessive external force from working. As such, each component positioned after the gear member 228 may be protected. Therefore, it is possible to prevent damage or breakage of each of the above components or the motor main body 92.

In addition, it is necessary to set only the strength of each component located after the gear member 228 based on the rotation transfer force (clutch release force) between the gear member 228 and the engaging plate 238. Therefore, it is not necessary to excessively set the strength of each component in consideration of excessive external force (load). As a result, manufacturing costs can be reduced.

In addition, since the clutch release of the clutch device 10 absorbs the shock applied to the driven component (for example, the wiper), the driven component (for example, the wiper) connected to the output shaft 12 is protected. Can be.

In the wiper motor device 290, the shaft 140 and the output shaft 12 provided as the swing center axis of the sector gear 192 are one side of the sector gear 132 in the thickness direction of the sector gear 132. It is connected to each other through a holding lever 138 disposed in. Therefore, the distance between shafts (inter-shaft pitch) between the shaft 140 and the output shaft 12 provided as the swing center axis of the sector gear 132 is kept constant. In addition, the gear tooth forming unit 136 of the sector gear 132 is a gear member located on the other side (combination plate 238 side) and the retaining lever 138 located on one side in the thickness direction of the sector gear 132. It is held between the connecting walls 235 of 228. Therefore, the engagement between the gear tooth 136 and the gear tooth forming portion 234 in the thickness direction of the sector gear 132 is limited. That is, wobbling in the thickness direction of the sector gear 132 does not require two holding members (holding levers) on both sides of the sector gear 132 in the thickness direction of the sector gear 132. Is prevented without. Accordingly, the engagement between the sector gear 132 and the gear member 228 is properly maintained.

In addition, in the wiper motor device 290, the holding lever 138 is disposed on the opposite side of the sector gear 132 which is located opposite from the worm wheel 128 in the thickness direction of the sector gear 132. Therefore, the retaining leisure 138 does not interfere with the worm wheel 128. Therefore, the design freedom of the connection position between the sector gear 132 and the worm wheel 128 is improved. That is, the design freedom of the installation position of the support shaft 134 relative to the worm wheel 128 is improved.

In addition, unlike the wiper motor device proposed in the wiper motor device 290, the holding member (holding lever) is not provided on the opposite side of the sector gear 132 in the thickness direction of the sector gear 132, respectively. . In other words, the single holding lever 138 in the wiper motor device 290 is disposed only on one side of the sector gear 132 in the thickness direction of the sector gear 132. Thus, the size and weight of the overall device configuration can be reduced.

As described above, in the wiper motor apparatus 290 of the fourth embodiment, the engagement between the sector gear 132 and the gear member 228 is properly maintained, and the size of the apparatus can be reduced.

Further, in the case of the above-mentioned wiper motor apparatus, when the holding member is disposed on the opposite side (the opposite side of the gear member) of the sector gear in the thickness direction of the sector gear, one of the holding members is a clutch device. Interfere with the engaging plate of the gear member. However, the retaining lever 138 in the wiper motor apparatus 290 of the fourth embodiment has the sector gear 132 opposed to the engaging plate 238 in the thickness direction of the sector gear 132 (the thickness direction of the gear member). It is provided only on the opposite side. Therefore, the holding lever 138 does not prevent the gear member 228 from engaging with the coupling plate 238. Thus, the position limitation of the clutch device 210 is relaxed.

In addition, in the wiper motor device 290, the coupling base 220 (large diameter portion) is fixedly connected to the rotational restraint portion 216 of the output shaft 12 formed with a projection. The coupling base 220 is firmly connected to the rotation restraint portion 216 of the output shaft 12, in particular in the direction of rotation about the axis. Movement of the gear member 228 from the output shaft 12 is limited by the movement limiting portion 218 of the output shaft 12. The coupling plate 238 is rotatably supported axially by the relative rotation limiting portion 214 of the output shaft 12 between the coupling base 220 and the gear member 228. Therefore, each corresponding component is installed in the output shaft 12, and the coupling plate 238 and the coil spring 244 are in a predetermined space (predetermined volume) between the coupling base 220 and the gear member 228. Is placed. As a result, as described above, the force (clutch release force) required for moving the engaging plate 238 in the axial direction can be easily set.

In addition, in the wiper motor device 290, the coil spring 244 is formed as an elastic member, the stable spring characteristics are achieved. In other words, when the rubber member is formed as an elastic member, grease or the like applied to the clutch device 210 is attached to the rubber member to age the rubber member. However, in the case of the coil spring 244, the coil spring 244 is not aged by grease or the like attached to the coil spring 244, so that the spring characteristic of the coil spring 244 is stabilized.

In addition, the coil spring 244 is wound in a spiral around the output shaft 12, the coupling plate 238 and the coupling base 220 that has a large diameter in the radial direction of the output shaft 12 and axially movable Is placed in between. Therefore, the coupling plate 238 can be pressed against the gear member 228 in a stable state, a stable resistance force can be applied. In other words, the coupling plate 238 may uniformly distribute the elastic force of the coil spring 244 at the engagement portion or connection portion between the gear member 228 and the coupling plate 238. Therefore, the engagement between the gear member 228 and the coupling plate 238 is stabilized, and the rotation transfer force (clutch release force) between the gear member 228 and the coupling plate 238 is stabilized. Therefore, stable clutch performance can be achieved, and the clutch release force can be set appropriately. As a result, each component of the wiper motor apparatus 290 can be more reliably protected.

In addition, in the wiper motor device 290, the gear member 228 supported by the output shaft 12 has an outer peripheral portion opposed to the gear teeth 234 with respect to the connecting wall 235, the cylindrical main surface 236 is formed. The cylindrical main surface 236 is rotatably supported by a bearing member 252 fixed to the housing 96. In other words, in the wiper motor apparatus 29, the gear member 228 that is loaded from the sector gear 132 is directly supported by the bearing member 252 of the housing 96. Therefore, the robustness of the support structure of the gear member is improved. In addition, the engagement between the gear member 228 and the sector gear 132 is stabilized. In addition, the base end of the output shaft 12 is supported by the housing (bearing member 252) through the gear member 228. Therefore, a dedicated space for supporting the base end of the output shaft 12 with respect to the housing 96 is not necessary. In other words, an accommodation space for accommodating the gear member 228 and a support space for supporting the base end of the output shaft 12 are common. In addition, between the bearing member 252 for supporting the base end of the output shaft 12 and the bearing member 250 for supporting the distal end of the output shaft 12 is measured in the axial direction of the output shaft 12 Relatively long axial distances are provided. This improves the robustness of the support structure of the output shaft 12 with respect to the housing 96.

Further, in the wiper motor device 290, each gear member 228 and the coupling plate 238 is made of a sintered metal product made through the molding of the powder alloy. Therefore, the gear member 2280 and the coupling plate 238 can be formed through a powder metallurgy process having a high precision and a good yield of material. 228 and the coupling plate 238 include lubricating oil in the sintered metal. Self-lubrication can be achieved at 242. In addition, self-lubrication is performed at the gear tooth 234 of the gear member 228 engaged with the gear tooth forming part 136 of the sector gear 132. To prevent wear and noise.

In addition, in the wiper motor device 290, the engagement projections 237 of the gear member 228 are different from each other in the peripheral direction of the gear member 228 (the spacing of adjacent engagement projections is different from each other). The coupling grooves 242 of the coupling plate 238 are disposed at different intervals (the spacing of adjacent coupling grooves is different from each other) in the peripheral direction of the coupling plate 238. In the clutch release state in which the engagement protrusions 237 are moved from the corresponding engagement grooves 242, the coupling plate 238 is engaged with the gear member 228 through at least three engagement protrusions 237 ( Three support points). Therefore, the engaged state between the engaging plate 238 and the gear member 228 is stabilized to the clutch released state.

In addition, the gear member 228 and the engaging plate 238 (output shaft 12 and wiper) are engaged with each other only at a predetermined single peripheral point. Therefore, in the clutch release state in which the gear member 228 and the engaging plate 238 are positioned at a position other than a predetermined single point, and thus each engaging protrusion 237 is moved from the corresponding engaging groove 242. When the wiper is manually rotated, for example by a vehicle operator, the gear member 228 and the engaging plate 238 are always meshed with each other at a predetermined point. Therefore, the coupling plate 238 (output shaft 12 and wiper) can be smoothly and quickly returned to the original setting state (initial setting state) with respect to the gear member 228. In addition, the wiper system can be operated again without damaging the wiper system. In particular, the predetermined single point of the reciprocating rotation angle range (reciprocating rotation wiping angle range) is set such that the predetermined single point is smaller than the limit angle range limited by the rotation limiting portions 144 and 146 of the stopper protrusion 142. When set to, the gear member 228 and engagement plate 238 engage each other again within a single reciprocating wiping movement of the wiper when the wiper system resumes its operation upon removal of excessive external force. To achieve self-recovery.

In addition, the clutch device 210 of the wiper motor device 290, the gear member 228 is a speed reduced by the swing device 94 (worm gear 122, worm wheel 128 and sector gear 1220) Therefore, the output shaft 12 can be driven by a relatively large torque, so that the wiper connected to the output shaft 12 can be smoothly reciprocated.

Accordingly, the wiper motor device 290 is applied to the output shaft 12 through the wiper when the wiper arm is applied to the wiper arm as a large amount of snow accumulated on the roof of the vehicle falls vertically along the window glass surface. It is suitable as a wiper motor device 290 of a vehicle such as a truck or a construction machine having a high probability cap-over type cockpit to be applied.

In addition, in the clutch device 210 of the wiper motor device 29, the engaging projection 237 of the gear member 228 is coupled to the coupling plate to transfer the rotational force from the gear member 228 to the coupling plate 238 ( 238 is received in the engagement groove 242. Therefore, the transmission of the driving force between the gear member 228 and the engaging plate 238 is surely executed. In addition, the side wall 237a of the coupling plate 237 of the gear member 228 and the side wall 242a of the engagement groove 242 of the coupling plate 238 have an inclined surface, and the clutch release force is determined by the angle of the inclined surface and The coil spring 244 can be easily set based on the resistance force (elastic deformation force).

Further, in the wiper motor apparatus 290, in the normal operating state (rotation state) as described above, when the rotation force is transmitted from the gear member 228 to the output shaft 12, the rotation driving force is related component It can be delivered without any sliding motion of. More specifically, the coil acting against the axial movement of the coupling plate 238 to maintain the mating state between the engaging projection 237 of the gear member 228 and the engaging groove 242 of the coupling plate 238 The resistance of the spring 244 is not consumed by sliding friction. Therefore, the decrease in rotational transfer efficiency can be prevented. In addition, the rotational driving force can be transmitted without generating the sliding motion of the corresponding component, so that noise generated by the sliding movement of the corresponding component can be effectively prevented.

In addition, as described above, the resistance of the coil spring 244 acting against the axial movement of the coupling plate 238 to maintain the engagement state between the engaging projection 237 and the engaging groove 242 is the output shaft ( A coupling base 220 fixed to 12 is received, and a gear member 228 supported by the output shaft 12 is received in the axial direction of the gear member 228 from the output shaft 12. Movement is prevented. That is, the force for maintaining the engaged state is supported by two components, that is, the coupling base 220 and the gear member 228 installed on the output shaft 12. In other words, it is completed as a subassembly of the output shaft 12 that does not require any additional components such as the housing 96 to serve as a sub-assembly. Therefore, the clutch device 210 can be treated as a single component formed as a subassembly of the output shaft 12.

As described above, in the wiper motor device 290 (clutch device 210) of the fourth embodiment, proper engagement between the sector gear 132 and the gear member 228 can be maintained, and the size of the device can be reduced. Can be.

In the fourth embodiment, the gear member 228 and the coupling plate 238 are made of a sintered metal product including lubricating oil. However, the present invention is not limited thereto. For example, only one of the gear member 228 and the coupling plate 238 may be made of a sintered metal product including lubricating oil.

Further, in the fourth embodiment, the wiper motor device 290 includes both the swing device 94 and the clutch device 210. However, the present invention is not limited thereto. For example, the clutch device may be omitted from the wiper motor device. In this case, the gear member may be provided integrally with the output shaft so as not to be movable in the axial direction with respect to the output shaft.

In the above embodiments, the first engagement 34, 36, 237 of the input disc 28, 128, 228 is a male engagement 34, 36, 237 protruding in the axial direction of the output shaft 12. Formed as In addition, the second engagement portions 50, 52, 242 of the clutch discs 38, 64, 238 are female engagement portions 50, 52, 242, which are formed in a groove shape in the axial direction of the output shaft 12. Is formed. However, the present invention is not limited to this configuration. For example, the first engagement portions 34, 36, 237 of the input disks 28, 128, 228 are grooves formed in the grooves on the input disks 28, 128, 228 in the axial direction of the output shaft. It can be formed as. Further, the second side engagement portions 50, 52, 242 of the clutch discs 38, 64, 238 protrude from the clutch discs 38, 64, 238 in the axial direction of the clutch discs 38, 64, 238. Can be formed into projections.

Further, in the above-described embodiments, when the load acting on the output shaft 12 is equal to or greater than a predetermined value, the input disk and the clutch disk are separated from each other, so that relative rotation occurs between the input disk and the clutch disk. . This overload acts not only as an overload acting as a rotating input disc, but also as an overload acting as a stationary output shaft when the input disc rotates (e.g., as an output shaft connected to a wiper frozen on the window pane in winter). Overload).

The present invention described above is not limited to the above-described embodiments and the accompanying drawings, and various substitutions, modifications, and alterations are possible within the scope without departing from the technical spirit of the present invention. It will be evident to those who have knowledge of.

As described above, the present invention can prevent damage to each component of the clutch device, the motor device, and the wiper system, and has the effect of preventing damage to the motor device.

Further, the clutch device, the motor device and the wiper system of the present invention reconnect the output shaft to the motor side component at a predetermined point so that normal operation can be performed even when a relative rotation occurs between the output shaft and the motor side component. In order to operate the motor-side components, the clutch device can be automatically returned to its initial position.

Claims (18)

A first rotating member reciprocatingly rotated by driving force; A second rotation capable of engaging with the first rotating member at the maximum rotational coupling force so as to rotate integrally with the first rotating member without generating a relative rotation between the first rotating member when the first rotating member reciprocates; absence; An output shaft connected to the second rotating member to be integrally rotated with the second rotating member and rotatable within a normal reciprocating rotation angle range; And At least one rotational limiter for limiting reciprocation of the output shaft beyond a limited rotational angle range greater than a normal reciprocal rotational angle range of the output shaft; Clutch device comprising a, A housing accommodating the clutch device; A motor body connected to the clutch device to provide a driving force to the first rotating member of the clutch device, Initial coupling at the maximum rotational coupling force between the first and second rotary members without generating relative rotation between the first and second rotary members is such that the output shaft is a normal reciprocating rotation of the output shaft. Only if it is located at a single joinable point in the angular range; When the load acting as the output shaft is greater than or equal to a predetermined value, the first rotating member and the second rotating member are separated from each other, and a relative rotation is generated between the first rotating member and the second rotating member; The housing includes a stopper protrusion integrally formed inside the housing at an inner surface of the housing in which the clutch device is accommodated; The one or more rotational limitations are integrally formed in the stopper protrusion of the housing; At least one of the second rotating member and the output shaft is directly or indirectly coupled to one of the one or more rotating limiters integrally formed in the stopper protrusion, and the reciprocating rotation of the second rotating member is limited. Motor unit. The method of claim 1, The first rotating member, the second rotating member and the output shaft are coaxial; The second rotating member is axially movable relative to the first rotating member; When the first rotation member and the second rotation member are coupled to each other at the maximum rotation coupling force without generating a relative rotation between the first rotation member and the second rotation member, the second rotation member is positioned at a first shaft position. Located; When the first rotating member and the second rotating member are separated from each other such that relative rotation occurs between the first rotating member and the second rotating member, the second rotating member is moved from the first shaft position. Located in the axis position of 2 Motor unit. The method of claim 1, The engageable point is located within a corresponding angle range starting from one or more peripheral edges of the limiting angle range and having an angular extension equal to the normal reciprocating rotational angle of the output shaft. Motor unit. The method of claim 1, The normal reciprocating rotation angle range of the output shaft is 170 degrees, The limit angle range is 180 degrees Motor unit. The method of claim 1, The first rotating member is connected to the output shaft at one end side of the output shaft in such a manner that the first rotating member is not axially separated from the output shaft and can be rotated reciprocally with respect to the axial direction of the output shaft. Supported by; The first rotating member has one or more first side engagement portions; The second rotating member is located on the other end side of the output shaft with respect to the first rotating member in such a manner that the second rotating member is not rotated with respect to the output shaft and is axially movable relative to the output shaft. Supported by the output shaft; The second rotating member may be formed at a single engagement point such that the first rotating member and the second rotating member are coupled to each other without generating a relative rotation between the first and second rotating members, and at the maximum rotational coupling force. At least one second side engagement portion engaged with at least one first side engagement portion of the first rotating member in the axial direction of the output shaft, An axial movement of the second rotating member disposed at the other end side of the second rotating member and coupled to each other such that the one or more first side engaging portions and the one or more second side engaging portions rotate together. Further comprising at least one elastic member for applying a resistance to the other end side of the output shaft with respect to Motor unit. The method of claim 5, The at least one first side engagement portion comprises a pair of first first engagement portions and a pair of second first engagement portions; The pair of first first engagement portions are located at positions 180 degrees apart from each other in the circumferential direction of the first rotating member; The pair of second first side engagement portions are positioned at positions 180 degrees apart from each other in the circumferential direction of the first rotating member; Wherein the pair of first first engagement portions are positioned at a position beyond the pair of second first engagement portions radially outwardly of the first rotating member; Motor unit. The method of claim 5, The output shaft includes a base member engaged with the second rotation member, and the second rotation member is integrally rotated with the base member; One of the second rotating member and the base member includes one or more numerical mating portions projecting in the radial direction of the output shaft; The other one of the second rotating member and the base member has at least one female fitting guide portion for receiving the at least one engagement portion in the axial direction of the output shaft, the peripheral wall extending in the axial direction of the output shaft And the at least one male engagement portion is axially movable relative to the at least one female fitting guide portion. Motor unit. The method of claim 7, wherein The one or more numerical fitting portions protrude radially outwardly of one of the second rotating member and the base member; The one or more rotational limitations are located in the rotational movement path of one of the one or more numerical engagement portions; One of the at least one number engagement portion is directly or indirectly engageable with the at least one rotation restriction portion to limit reciprocation of the output shaft exceeding the limit angle range. Motor unit. The method of claim 5, A base member which is axially immovable with respect to the output shaft and is supported by the output shaft so as not to be rotatable relative to the output shaft; The base member includes a stopper portion projecting radially outward from the base member; The stopper portion of the base member is directly or indirectly engaged with the at least one rotational restriction portion to limit the reciprocating rotation of the output shaft exceeding the limiting angle range; The at least one elastic member includes a compression coil spring which is wound in a compressed state and spirally wound about an axis of the output shaft between the second rotating member and the base member. Motor unit. The method of claim 1, The second rotating member is engageable with the first rotating member at a reduced rotational coupling force smaller than the maximum rotational coupling force so that the second rotating member rotates along the first rotating member when the first rotating member is reciprocated. Motor unit. delete delete The method of claim 1, And a worm gear provided on the rotating shaft of the motor main body so as to be integrally rotated with the rotating shaft, wherein the first rotating member of the clutch device is directly engaged with the worm gear and rotated at a reduced speed. Motor unit. The method of claim 1, The housing rotatably supports the output shaft; One of the first rotating member and the second rotating member of the clutch device has a diameter larger than the diameter of the other of the first rotating member and the second rotating member, and has a cylindrical peripheral surface coaxial with the output shaft. To; The bearing member is fixed to the housing to rotatably support the cylindrical peripheral surface of one of the first rotating member and the second rotating member Motor unit. The method of claim 1, Used for wiper systems including wipers; Further comprising a motion converter, wherein the motion converter A worm gear provided on the rotating shaft of the motor main body to be integrally rotated with the rotating shaft; A worm wheel engaged with the worm gear and rotating about a rotation axis extending in a direction orthogonal to the axis of the rotation shaft; One end is connected to the worm wheel at a position spaced apart from the rotation axis of the worm wheel, the other end is engaged with the first rotating member of the clutch device, and reciprocating swing by the rotation of the worm wheel to reciprocally rotate the first rotating member And a swing member for reciprocating the wiper directly or indirectly connected to the output shaft. Motor unit. The motor device according to claim 1; And A wiper connected directly or indirectly to an output shaft of the clutch device and reciprocally swinging when the output shaft reciprocates. Wiper system. The method of claim 16, Further comprising a motion converter, wherein the motion converter A worm gear provided on the rotating shaft of the motor main body to be integrally rotated with the rotating shaft; A worm wheel meshed with the worm gear and rotated about a rotation axis orthogonal to the axis of the rotation shaft; And One end is connected to the worm wheel at a position spaced apart from the rotation axis of the worm wheel, the other end is engaged with the first rotation member of the clutch device, and reciprocating swing by the rotation of the worm wheel to reciprocally rotate the first rotation member A swing member Wiper system. The method of claim 16, The fixed strength between the output shaft and the second rotating member in the rotational direction of the output shaft is greater than the connection strength of the wiper to the output shaft directly connected to the wiper in the rotational direction of the output shaft. Wiper system.

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